US11143259B2 - Vibration absorber - Google Patents

Vibration absorber Download PDF

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Publication number
US11143259B2
US11143259B2 US16/825,362 US202016825362A US11143259B2 US 11143259 B2 US11143259 B2 US 11143259B2 US 202016825362 A US202016825362 A US 202016825362A US 11143259 B2 US11143259 B2 US 11143259B2
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Prior art keywords
vibration absorber
opening
supporting bodies
absorber
spring elements
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US16/825,362
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US20200309226A1 (en
Inventor
Markus Dürre
Thomas Bock
Frederik Goetz
Karsten Terhardt
Christian Paul
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Vibracoustic SE
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Vibracoustic SE
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Assigned to VIBRACOUSTIC AG reassignment VIBRACOUSTIC AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GOETZ, FREDERIK, BOCK, THOMAS, DURRE, MARKUS, PAUL, CHRISTIAN, TERHARDT, KARSTEN
Publication of US20200309226A1 publication Critical patent/US20200309226A1/en
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Assigned to VIBRACOUSTIC SE reassignment VIBRACOUSTIC SE CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: VIBRACOUSTIC AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • F16F7/108—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on plastics springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/373—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape
    • F16F1/3732—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape having an annular or the like shape, e.g. grommet-type resilient mountings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal

Definitions

  • the invention relates to a vibration absorber for absorbing and/or damping vibrations of a vehicle part, comprising at least one absorber mass having an opening and at least two spring devices which are inserted into the opening.
  • Vibration absorbers of the type mentioned above may be used to reduce vibrations transmitted from the engine to a part of the vehicle, such as a gearbox, while the vehicle is in motion or at a standstill, which may increase travelling comfort.
  • Some vibration absorbers may have a spring device composed of elastomeric material, and a mass element, the mass element being coupled to the vehicle part to be damped in a manner so as to be capable of vibrating. When a vehicle part connected to the vibration absorber starts to vibrate, the absorber mass resonates with a 90° phase shift, wherein the vibrations are damped by the spring device.
  • the three linear rigid body resonances should, at least in some circumstances, have the same frequency or a certain ratio to each other.
  • Conventional vibration absorbers with radially or axially arranged spring devices can only be adjusted in a very limited frequency ratio, which is related to the physical properties of the elastomer with regard to tension-compression stiffness and shear stiffness.
  • Embodiments of the present disclosure may include a vibration absorber which has an improved adjustable frequency ratio in the high frequency range and is also cost-effective.
  • a vibration absorber in particular a modular vibration absorber, for absorbing and/or damping vibrations of a vehicle part, may comprise at least one absorber mass having an opening and/or at least two spring devices which are inserted into the opening.
  • Each of the spring devices may have at least one elastomeric spring element and a supporting body.
  • the supporting body may receive the spring element.
  • the supporting body may have an insertion section for inserting the supporting body and the spring element into the opening, which may be inclined relative to a longitudinal axis of the vibration absorber.
  • the supporting bodies may have an insertion section that is inclined with respect to the longitudinal axis of the vibration absorber, so a frequency spread between radial and axial resonance frequency may be set so that the frequency ratio of the vibration absorber can be specifically adjusted in a high-frequency range.
  • the insertion section may be inclined at an angle to the longitudinal axis of the vibration absorber.
  • the angle may also be referred to as the inclination angle.
  • the angle, or inclination angle is the angle that the inclined surface of the insertion section forms with the longitudinal axis. This angle may depend on the frequency to be adjusted. A radial and axial frequency spread may be adjusted via the angle. In embodiments, the angle may be greater than 0° and/or less than 90°.
  • the spring element may be received by the supporting body in such a way that the spring element surrounds the supporting body, such as on the outer circumference.
  • the supporting body may also be described as a fixing element, as it may fix the spring element to the absorber mass. In embodiments, the supporting body may fix the spring element to the absorber mass.
  • a supporting body may receive the spring element, which may allow for manufacturing the elastomeric spring element separately.
  • an elastomeric shaped part may be used as a spring element which can be adjusted specifically to a desired frequency ratio.
  • the manufacturing costs of the vibration damper may be reduced, such as because preheating of the damper mass, which may be necessary for vulcanizing an elastomeric spring device, may no longer be required.
  • the elastomer spring elements may be manufactured with a high tool cavity.
  • a vibration absorber may be created in the form of a modular kit.
  • Spring elements with different properties such as different Shore hardnesses, and supporting bodies with different inclination angles and mass-external geometries may be used.
  • the opening may include a through hole that may extend from a first end of the absorber mass to a second end of the absorber mass.
  • the absorber mass may have two openings and a spring device may be inserted into one or both openings.
  • a first spring device may be inserted into the opening at a first end of the absorber mass and/or a second spring device may be inserted into the opening at a second end of the absorber mass.
  • the spring devices may be inserted opposite each other in the opening.
  • the opening at both ends of the absorber mass may include an insertion bevel that may correspond to inclined insertion sections and/or a contour of the spring elements.
  • the supporting bodies may, for example and without limitation, be made of metal and/or plastic. Some or all of the supporting bodies may have a hole through which a fastening element can be passed in order to connect the vibration absorber to a vehicle part.
  • the fastening element may extend through the opening and the holes for fastening to a vehicle part.
  • the absorber mass may be made of metal and/or may be cylindrical.
  • a vibration absorber may be used, for example, for absorbing and/or damping a vehicle part, such as a gearbox, tailgate or chassis.
  • the opening may have insertion bevels that may be formed to correspond to inclined insertion sections and/or to a contour of the spring elements, which may facilitate insertion of the supporting bodies together with the spring elements. Additionally or alternatively, the insertion bevels may facilitate adjusting the frequency spread between radial and axial resonance frequency.
  • the opening may widen conically towards both end faces of the absorber mass.
  • the insertion bevels may be inclined in relation to the longitudinal axis of the vibration absorber.
  • the insertion bevels form an angle with the longitudinal axis of the vibration absorber.
  • the angle of the insertion bevels may also be referred to as the inclination angle.
  • the angle for example, may be greater than 0° and/or less than 90°.
  • the angle of the insertion bevels may correspond to the angles of the insertion sections. Additionally or alternatively, the angles of the insertion bevels and the angles of the insertion sections may be different.
  • the spring elements may be connected to the supporting bodies and/or the absorber mass in a positive fit, non-positive-fit, and/or substance-to-substance bond, which may allow a simple and cost-effective attachment of the spring elements to the supporting bodies and/or the absorber mass.
  • the spring elements may be placed or slid onto the supporting body with a positive and/or non-positive fit.
  • the spring elements may be connected to the supporting bodies in such a way that the spring elements surround the outer circumference of the supporting bodies.
  • the elastomeric spring elements may be connected to the supporting bodies and/or the absorber mass in a substance-to-substance bond.
  • the supporting bodies and/or the absorber mass may be placed in an injection mold and/or the spring elements may be injected onto the supporting bodies and/or the absorber mass.
  • the spring elements may be funnel-shaped, which may allow the frequency spread between the radial and axial resonant frequency of the spring elements to be specifically adjusted.
  • An inclination angle of the spring elements may correspond to the inclination angle of the insertion sections and/or the inclination angle of the insertion bevels of the opening.
  • the spring elements may have a funnel portion corresponding to the insertion bevels and the insertion sections, and a sleeve section corresponding to a cylindrical section of the supporting bodies.
  • an inner circumferential contour of the spring elements may correspond to an outer circumferential contour of the supporting bodies so that the spring elements enclose the outer circumference of the supporting bodies.
  • some or all of the supporting bodies may have a cylindrical portion adjacent to the insertion section, the outer diameter of which may be larger than an inner diameter of the opening.
  • the cylindrical section may act as a loss prevention device that may prevent and/or restrict the absorber mass from falling off in the event of failure of rubber or bond.
  • the two spring devices may be connected to each other by a fastening sleeve extending through the opening.
  • the fastening sleeve may fasten the two spring devices, which may be inserted at the end of the opening, to the absorber mass.
  • the fastening sleeve may extend through the opening.
  • an outer diameter of the fastening sleeve may be smaller than an inner diameter of the opening. This may keep the fastening sleeve at a distance from the absorber mass, which may allow the absorber mass to move relative to the fastening sleeve, such as to absorb and/or to damp vibrations.
  • the vibration absorber may be fastened to a vehicle part via the fastening sleeve.
  • the fastening sleeve may have a passage through which a fixing element may extend.
  • the sleeve may be made of metal and/or plastic, for example.
  • a fastening sleeve may be connected to the supporting bodies with a positive and/or non-positive fit. This may provide a simple and cost-effective way of fastening the supporting bodies via the fastening sleeve. Some or all of the supporting bodies may have a hole into which the fastening sleeve may be inserted with a positive and/or non-positive fit, with the fastening sleeve extending through the opening.
  • a non-positive fit between the spring devices and the fastening sleeve may be achieved during the fastening of the vibration absorber to an adjacent vehicle part by means of a positive fit.
  • An interference fit between the fastening sleeve and the supporting bodies may be secured by a positive fit between a fastening element and a contact surface of a motor vehicle component, such as in the final assembly. Securing by a positive fit may, for example, allow for the use of plastic for the supporting bodies.
  • the spring elements of the spring devices may be connected to each other.
  • the two spring elements may be made of the same material and/or may be designed in one piece. This may allow the spring elements to be manufactured in a vulcanization process.
  • the spring elements may be manufactured in the form of an elastomeric hose or a rubber plate.
  • the insertion sections of the supporting bodies may be inclined at different angles in relation to a longitudinal axis of the vibration absorber.
  • the supporting bodies may have different inclination angles.
  • the adjusting ratio of the two spring devices and thus, the frequency spread between radial and axial resonance frequency may be different. With such a configuration, for example, asymmetric spreading of masses can be balanced.
  • FIG. 1 is a cross-sectional view of a vibration absorber according to an embodiment in an unassembled condition.
  • FIG. 2 is a cross-sectional view of an embodiment of a spring device.
  • FIG. 3 is a cross-sectional view of the embodiment of a vibration damper shown in FIG. 1 in a mounted condition.
  • FIG. 4 is a cross-sectional view of the embodiment of a vibration damper shown in FIG. 3 , which is fastened to a vehicle part.
  • FIG. 5 is a cross-sectional view of a vibration absorber according to an embodiment in unassembled condition.
  • FIGS. 1, 3 and 4 show a vibration absorber 10 according to a first embodiment, which may be used to absorb and/or damp vibrations, such as vibrations of a vehicle part 12 .
  • a vibration absorber 10 may have an absorber mass 14 , a plurality (e.g., two) spring devices 16 , and/or a fastening sleeve 18 .
  • the fastening sleeve 18 may be configured for fixing the two spring devices 16 to the absorber mass and/or to the vehicle part 12 .
  • the absorber mass 14 may be made of metal and may have a substantially cylindrical shape.
  • An opening 20 may be introduced in the absorber mass.
  • the opening 20 may extend from a first end 22 of the absorber mass 14 to a second end 24 of the absorber mass 14 .
  • the opening 20 may be provided with an insertion bevel 26 at one or both ends 22 , 24 .
  • the insertion bevels 26 may be inclined relative to a longitudinal axis L of the vibration absorber 10 .
  • the insertion bevels 26 may form an angle ⁇ , which may be referred to as the inclination angle, with the longitudinal axis L.
  • the angle ⁇ may, for example and without limitation, be greater than 0° and/or less than 90°.
  • the fastening sleeve 18 may include a metal sleeve that extends through the opening 20 .
  • an outer diameter of the fastening sleeve 18 may be smaller than an inner diameter of the opening 20 so that the absorber mass 14 can move relative to the fastening sleeve 18 , such as to absorb and/or damp vibrations, such as vibrations of a vehicle part 12 .
  • a fastening sleeve 18 may be utilized to fasten the vibration absorber 10 to the vehicle part 12 .
  • the fastening sleeve 18 may have a passage 28 through which the fastening element 30 (see, e.g., FIG. 4 ) may extend.
  • the fastening element 30 may, for example, be designed as a hexagon head screwed into a threaded hole 32 that may be provided in the vehicle part 12 .
  • some or each of the spring devices 16 may have a supporting body 34 and an elastomeric spring element 36 that may be received by the supporting body 34 , such as by connecting the spring element 36 to the supporting body 34 in a positive fit, non-positive-fit, and/or substance-to-substance bond.
  • a supporting body 34 may, for example and without limitation, include metal and/or plastic.
  • the supporting body 34 may have an insertion section 38 for inserting the supporting body 34 and the spring element 36 into the opening 20 .
  • the insertion section 38 may be inclined relative to the longitudinal axis L of the vibration absorber 10 .
  • the insertion section 38 may form an angle ⁇ , which may also be referred to as the inclination angle, with the longitudinal axis L.
  • the angle ⁇ may, for example and without limitation, be greater than 0° and/or less than 90°.
  • the two angles ⁇ and ⁇ may be of substantially equal size.
  • a cylindrical section 40 may be arranged adjacent to the insertion section 38 .
  • the outer diameter of the cylindrical section may, for example, be larger than an inner diameter of the opening 20 .
  • the supporting body 34 e.g., cylindrical section 40
  • the supporting body 34 may form a loss prevention that may prevent and/or restrict the absorber mass 14 from falling off.
  • the supporting body 34 may have a bore hole 42 into which the fastening sleeve may be inserted, such as with a positive and/or non-positive fit.
  • the spring element 36 may be designed as a separately produced elastomeric shaped part and may be generally funnel-shaped. With embodiments, such as generally illustrated in FIGS. 1 to 4 , the spring element 36 may have a funnel portion 44 corresponding to the insertion bevel 26 and the insertion section 38 , and/or a sleeve section 46 corresponding to the cylindrical section 40 .
  • an inner circumferential contour of the spring element 36 may correspond to an outer circumferential contour of the supporting body 34 , so that the spring element 36 encloses the outer circumference of the supporting body 34 (see, e.g., FIG. 2 ).
  • a vibration absorber 10 may be mounted with or on a vehicle part 12 .
  • the spring elements 36 may first be placed, in particular pressed, onto the supporting bodies 34 to form two spring devices 16 .
  • the fastening sleeve 18 may be inserted into the opening 20 .
  • the spring devices 16 may be slid onto the fastening sleeve 18 .
  • the fastening element 30 may be inserted into the passage 28 and/or screwed into a threaded bore hole 32 of the vehicle part 12 .
  • a non-positive fit between the fastening sleeve 18 and the supporting bodies 34 may, for example and without limitation, only be secured by a positive fit between a head of the fastening element 30 and a contact surface of the vehicle part 12 in the final assembly.
  • the supporting body 34 may have an insertion section 38 that may be inclined relative to the longitudinal axis L of the vibration absorber 10 , which may allow for a frequency spread between radial and axial resonance frequency to be adjusted, for example, so that the frequency ratio of the vibration absorber 10 can be specifically adjusted in a high-frequency range.
  • the spring element 36 may be manufactured separately as a low-cost elastomeric shaped part with a high tool expertise.
  • FIG. 5 generally illustrates a second embodiment of a vibration absorber 10 , which differs from the first embodiment in that the spring elements 36 may be connected to the supporting bodies 34 in a substance-to-substance bond.
  • the supporting bodies 34 may placed in an injection mold, and the spring elements 36 may be injection-molded onto/with the supporting bodies 34 .
  • a vibration absorber 10 may include inclined insertion sections 38 of the supporting bodies 34 , which may allow for a frequency spread between radial and axial resonance frequency to be adjusted, while the spring elements 36 may be produced as separate and cost-effective elastomer moldings. Additionally or alternatively, a vibration absorber 10 may be created/provided in the form of a modular kit, as spring elements 36 with different properties, such as different Shore hardnesses, and support bodies 34 with different inclination angles ⁇ , may be used.
  • references to a single element are not necessarily so limited and may include one or more of such element.
  • Any directional references e.g., plus, minus, upper, lower, upward, downward, left, right, leftward, rightward, top, bottom, above, below, vertical, horizontal, clockwise, and counterclockwise
  • Any directional references are only used for identification purposes to aid the reader's understanding of the present disclosure, and do not create limitations, particularly as to the position, orientation, or use of examples/embodiments.
  • joinder references are to be construed broadly and may include intermediate members between a connection of elements and relative movement between elements. As such, joinder references do not necessarily imply that two elements are directly connected/coupled and in fixed relation to each other.
  • the use of “e.g.” in the specification is to be construed broadly and is used to provide non-limiting examples of embodiments of the disclosure, and the disclosure is not limited to such examples.
  • Uses of “and” and “or” are to be construed broadly (e.g., to be treated as “and/or”). For example and without limitation, uses of “and” do not necessarily require all elements or features listed, and uses of “or” are inclusive unless such a construction would be illogical.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Vibration Prevention Devices (AREA)
  • Springs (AREA)
US16/825,362 2019-03-27 2020-03-20 Vibration absorber Active US11143259B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019107885.7 2019-03-27
DE102019107885.7A DE102019107885B4 (de) 2019-03-27 2019-03-27 Schwingungstilger

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US20200309226A1 US20200309226A1 (en) 2020-10-01
US11143259B2 true US11143259B2 (en) 2021-10-12

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DE (1) DE102019107885B4 (de)

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DE102019104386A1 (de) * 2019-02-21 2020-08-27 Vibracoustic Ag Schwingungstilger
DE102019125701B4 (de) * 2019-09-24 2023-01-26 Vibracoustic Se Dämpfungsvorrichtung sowie Verfahren zu dessen Montage
DE102020128549A1 (de) 2020-10-29 2022-05-05 Böllhoff Verbindungstechnik GmbH Dämpfungsanordnung, Bauteil mit Dämpfungsanordnung sowie entsprechende Bauteilverbindung, ein Herstellungsverfahren und ein Verbindungsverfahren
DE102022110271A1 (de) 2022-04-27 2023-11-02 Böllhoff Verbindungstechnik GmbH Dämpfungsanordnung, Bauteil mit Dämpfungsanordnung, entsprechende Bauteilverbindung, Verbindungsverfahren und Herstellungsverfahren

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CN111750027A (zh) 2020-10-09
DE102019107885B4 (de) 2023-09-21

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